Compound type heat exchanger

ABSTRACT

In a compound type heat exchanger A 1 , a first heat exchanger  1  includes a pair of long tanks  3, 4  arranged a certain distance apart from each other and a core part  5  having tubes  5   a  between the both tanks  3, 4 . The tank  3  is composed of a plurality of divided bodies  6  to  8  that are connected along a longitudinal direction of the tank  3 . The divided body  7  is provided with an accommodation portion  9  that projects outwardly to communicate with the certain divided body  7 . A second heat exchanger  2  is arranged in the accommodation portion  9 , which is provided with an input port P 3 . Heat is exchanged between an intake air of the first heat exchanger  1  that flows in the accommodation portion  9  and a coolant of the second heat exchanger  2.

TECHNICAL FIELD

The present invention relates to a compound type heat exchanger where afirst exchanger and a second heat exchanger are joined with each other.

BACKGROUND OF THE INVENTION

A Patent document 1 discloses a technology of a compound type heatexchanger. In this invention, a first heat exchanger contains a secondheat exchanger.

-   Patent Document 1: U.S. Pat. No. 6,755,158

DISCLOSURE OF THE INVENTION Problem(S) to be Solved by the Invention

However, in the prior invention, in a case where the temperature of theintake air flowing in the tubes of the first heat exchanger is differentamong them, a heat stress generates due to the distribution of thetemperature in the core portion and consequently the durability in theroot portions of the tubes and others might deteriorate.

In order to remove the problem, the core part of the second heatexchanger needs to be arranged in a state where it is arranged near allof the tubes of the first heat exchanger so as to face thereto, as thesecond heat exchanger is contained in the first heat exchanger. Thisbrings the second heat exchanger to be larger in size.

In other words, in a case where the entire length of the second heatexchanger is set shorter, a part of the flowing medium of the first heatexchanger flows in the tubes of the first heat exchanger without heatexchange with that of the second heat exchangers, and thereby theflowing medium with the temperature different in the tubes flows in. Asa result, the heat stress generates due to the distribution of thetemperature, and thereby there is a possibility of the deterioration inits durability of the first heat exchanger.

Accordingly, there is a problem in that the design freedom of the firstheat exchanger and the second heat exchanger is limited to a smallextent and the design change of the first heat exchanger and the secondheat exchanger is needed to a large extent for every kind thereof in acase of manufacturing many kinds of the first heat exchangers whose theheights of the core parts are different for examples.

The present invention is made to solve the above-described problem, andits object is to provide a compound type heat exchanger whose designfreedom can be increased.

Means for Solving the Problems

The compound type heat exchanger of the present invention includes:

a first heat exchanger including a pair of long tanks arranged a certaindistance apart from each other and a core part having tubes and finsalternately piled up between the tanks, whereinat least one of tanks is constituted of a plurality of divided bodiesthat are connected along a longitudinal direction of the at-least one ofthe tanks, whereina certain divided body of the plurality of divided bodies is providedwith an accommodation portion that projects outwardly and is connectedwith the certain divided body, whereina second heat exchanger is arranged in the accommodation portion,whereinthe accommodation portion is provided with a connection port as agateway of the flowing medium of the first heat exchanger, and whereinheat is exchanged between the flowing medium of the first heat exchangerthat flows thorough the accommodation portion and a flowing medium ofthe second heat exchanger.

Effect of the Invention

In the compound type heat exchanger of the present invention, the firstheat exchanger is composed of the plurality of the divided bodies, thecertain divided body being provided with the accommodation portion andthe second heat exchanger being arranged in the accommodation portion.Therefore, the design freedom of the first heat exchanger and the secondheat exchanger can be increased.

In addition, the certain divided body can employ common use parts, andonly the design change of the other divided bodies can easilyaccommodate many kinds of the first exchangers different in the heightsof their core parts.

Alternatively, only the design change of the certain divided body caneasily accommodate many kinds of the second heat exchangers different insize.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a front view showing a compound type heat exchanger of a firstembodiment of the present invention;

FIG. 2 is an exploded perspective view showing a relevant part of thecompound type heat exchanger of the first embodiment;

FIG. 3 is a front view of a second heat exchanger of the compound typeheat exchanger of the first embodiment;

FIG. 4 is a perspective view of the second heat exchanger shown in FIG.3;

FIG. 5 is a perspective view showing a main part of a tank of thecompound type heat exchanger of the first embodiment;

FIG. 6 is a front view showing the main part of the tank shown in FIG.5;

FIG. 7 is a left side view showing the main part of the tank shown inFIG. 5;

FIG. 8 is a right side view showing the main part of the tank shown inFIG. 5;

FIG. 9 is a view explaining how to fix the second heat exchanger in thecompound type heat exchanger of the first embodiment;

FIG. 10 is a view showing an interior of the tank shown in FIG. 5;

FIG. 11 is a view showing the states (a) before an insertion member isfixed to a tube and (b) after the insertion member is fixed to the tubein the compound type heat exchanger of the first embodiment;

FIG. 12 is a view showing an engine cooling circuit and a turbochargercircuit that use the compound type heat exchanger of the firstembodiment;

FIG. 13 is a view explaining the operation of the compound type heatexchanger of the first embodiment;

FIG. 14 is a view showing an interior of a tank that is used in acompound type heat exchanger of a second embodiment of the presentinvention; and

FIG. 15 is a perspective view showing a deformed portion of a tube thatis used in the compound type heat exchanger of the second embodiment.

DESCRIPTION OF REFERENCE NUMBERS

-   -   A1 compound type heat exchanger    -   A2 engine    -   A3 radiator    -   A4 thermostat    -   A5 water pump    -   A6 turbocharger    -   A7 EGR cooler    -   a1, a2, a3, a4, a5, a6, a7, a8, a9, a10, a11, a12, a13 passage    -   B1, B2 bolt    -   O1 clearance    -   O2 opening portion    -   P1, P3 input port    -   P2, P4 output port    -   R1, R2, R3 chamber    -   S1, S2 seal member    -   1 first heat exchanger    -   2 second heat exchanger    -   3, 4, 13, 14 tank    -   5, 15 core part    -   5 a, 5 c, 15 a tube    -   5 b, 15 b fin    -   6, 7, 8 divided body    -   6 a, 7 a, 8 a tube hole    -   7 b opening portion    -   9 accommodation portion    -   10 collection portion    -   10 a passage    -   11 projecting portion    -   11 a opening portion    -   11 b bolt hole    -   16 partition wall    -   17 obstruction member    -   17 a through-hole    -   18 base portion    -   18 a through-hole    -   19 seat portion    -   19 a opening portion    -   20, 21 discharge pipe    -   22 engine cooling circuit    -   23 turbocharger circuit    -   24 fan    -   30 insertion member    -   30 a insertion portion    -   30 b engagement portion    -   31 deformed portion

BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, the embodiments of the present invention will be explainedwith reference to the accompanied drawings.

First Embodiment

Hereinafter, a first embodiment of the present invention will bedescribed.

Incidentally, a vehicular front and rear direction and a vehicular widthdirection are respectively referred to as a front and rear direction anda left and right direction in the description below.

FIG. 1 is a front view showing a compound type heat exchanger of thefirst embodiment, FIG. 2 is an exploded perspective view showing arelevant part of the first embodiment, FIG. 3 is a front view showing asecond heat exchanger of the first embodiment, FIG. 4 is a perspectiveview of the same, and FIG. 5 is a perspective view showing a main partof a tank of the first embodiment.

FIG. 6 is a front view showing a main part of the tank that is used inthe compound type heat exchanger of the first embodiment, FIG. 7 is aleft side view of the tank, FIG. 8 is a right side view of the tank,FIG. 9 is a view explaining how to fix the second heat exchanger that isused in the compound type heat exchanger of the first embodiment, FIG.10 is view showing an interior of the tank, FIG. 11 is a view showingthe states (a) before an insertion member is fixed to a tube and (b)after the insertion member is fixed to the tube in the compound typeheat exchanger, FIG. 12 is a view showing an engine cooling circuit anda turbocharger circuit of the first embodiment, and FIG. 13 is a viewexplaining the operation of the compound type heat exchanger of thefirst embodiment.

First, the entire construction of the compound type heat exchanger ofthe first embodiment will be explained.

As shown in FIG. 1, the compound type heat exchanger A1 of the firstembodiment is equipped with a first heat exchanger 1, a second heatexchanger 2 and others.

The first heat exchanger 1 is an intercooler that is incorporated in aturbocharger circuit 23, which will be later described, and the firstheat exchanger 1 is provided with a pair of long tanks 3, 4 that arearranged a certain distance apart from each other in the right and leftdirection, and a core part 5 that is arranged between the both tanks 3,4. The core part 5 to includes a plurality of flat tubes 5 a inserted inand fixed to the both tanks 3, 4, and fins 5 b that are arranged beingstacked alternatively with the tubes 5 a and are formed like a waveplate whose wave-like top portions are joined on the adjacent tubes 5 a.

Incidentally, the fins 5 b may be removed.

In addition, a pair of upper and lower reinforcements may be provided atthe both sides of the core part 5 in its stack direction to be insertedin and fixed to the both tanks 3, 4.

Further, inner fins may be provided in the interiors of tubes 5 a.

As shown in FIG. 2, the tank 3 is composed of three divided bodies 6 to8 that are connected in a longitudinal direction.

The upper side divided body 6 is formed in a cylinder, having arectangular cross section and a bottom portion, which opens toward thedivided body 7, and the upper side divided body 6 is formed in its innerside with a plurality of tube holes 6 a equally spaced so that thecorresponding end portions of the tubes 5 a can be inserted in and fixedto the tube holes 6 a (refer to FIG. 7).

The lower divided body 8 is formed in a cylinder, having a rectangularcross section and a bottom portion, which opens toward the intermediatedivided body 7, and the lower side divided body 8 is formed in its innerside with a plurality of tube holes 8 a equally spaced so that thecorresponding end portions of the tubes 5 a can be inserted in and fixedto the tube holes 8 a (refer to FIG. 7).

The intermediate divided body 7 is formed in its inner side with aplurality of tube holes 7 a equally spaced so that the corresponding endportions of the tubes 5 a can be inserted in and fixed to the tube holes7 a (Five holes are illustrated in the first embodiment as shown in FIG.7).

Incidentally, each divided body 6 to 8 may be composed of a tube plateand a tank main body, where the tube plate is made of aluminum andshaped like a dish so that the tubes can be inserted in and fixed to thetube plate, and the tank main body is made of resin material and shapedlike a serving dish, being fixed by caulking with the tube plate in astate they are coupled with each other like a box, as well asconventional tanks of intercoolers made of resin material.

In addition, at the upper and lower sides of the intermediate dividedbody 7, opening portions 7 b (the lower opening portion is notillustrated) are formed to fit the outer profiles of the end portions ofthe divided bodies 6, 8, respectively.

In addition, at the outer side of the intermediate divided body 7, anaccommodation portion 9 is formed to have a shape projecting a reardirection through a collection part 10 extending in the left and rightdirection.

In the collection portion 10, narrow passages 10 a (refer to FIG. 9) areformed, and a projecting portion 11 is provided to have a rectangularshape, projecting rearward in a state where the projecting portion 11communicates with the passages 10 a.

At a rear surface of the projecting portion 11, a circular openingportion 11 a and a plurality of bolt holes 11 b (Three are illustratedin the first embodiment.) are formed.

Incidentally, the opening portion 11 a is formed slightly larger inopening diameter than an input port P3, which will be described.

As shown by a dashed line in FIG. 2, the second heat exchanger 2 isarranged in an inclined state in the projecting portion 11.

As shown in FIG. 3 and FIG. 4, the second heat exchanger 2 is equippedwith a pair of long tanks 13, 14 arranged a certain distance apart fromeach other in an upward and downward direction, and a core part 15arranged between the both tanks 13, 14.

The core part 15 includes a plurality of flat tubes 15 a inserted in andfixed to the both tanks 13, 14, and fins 15 b that are arranged beingstacked alternatively with the tubes 15 a and are formed like a waveplate whose wave-like top portions are joined on the adjacent tubes 15a.

Incidentally, the fins 15 b may be removed.

In addition, a pair of upper and lower reinforcements may be provided atthe both sides of the core part 15 in its stack direction to be insertedin and fixed to the both tanks 3, 4.

In addition, a partition wall 16 separates the interior of the uppertank 13 into two chambers, a first chamber R1 and a third chamber R3.Further, an input port P1 is provided in a state where it communicateswith the first chamber R1, while an output port P2 is provided in astate where it communicates with the third chamber R3.

Further, a second chamber R2 is provided in the interior of the lowertank 14.

In addition, the both ports P1, P2 are provided in a state where theypass through an obstruction member 17 shaped like a plate. As shown inFIG. 4, through-holes 17 a are formed at four corners of the obstructionmember 17, respectively.

As shown in FIG. 5 to FIG. 8, the end portions of the both dividedbodies 6, 8 are respectively inserted into the opening portions 7 bformed on the upper and lower surfaces of the intermediate divided body7 to certain extents, and then they are connected to integrally jointhese three parts.

In addition, on the front surface of the projecting portion 11, theinput port P1 is provided in a state where it faces to the openingportion 11, being fixed by bolts B1 being screwed into bolt holes 11 bthrough through-holes 18 a formed in its base portion 18 in a statewhere the base portion 18 of the input port P3 shown in FIG. 2 contactswith the front surface of the projecting portion 11.

Therefore, the input port P3 can be fixed on and detached from theaccommodation portion 9 from its exterior side.

Incidentally, on the rear surface of the base portion 18 of the inputport P3, a seal member S1 (illustrated by a heavy line in FIG. 5), whichis made of heat-resistance material and shaped like a sheet, is affixedto ensure a sealing performance of the interior of the accommodationportion 9.

Further, as shown in FIG. 9, the second heat exchanger 2 is insertedalong an oblique direction into the opening portion 19 a of the slantedseat portion 19 formed on the upper surface of the projecting portion 11to be in a state where the obstruction member 17 contacts with the seatportion 19. The second heat exchanger 2 is arranged in the projectingportion 11 in a diagonally suspended state, being fixed by bolts B2being screwed into not-shown bolt holes of the seat portion 19 throughthe through-holes 17 a of the obstruction member 17.

Therefore, the second heat exchanger 2 can be fixed to and detached fromthe accommodation portion 9 from the exterior side.

Incidentally, on the rear surface of the obstruction member 17 of theinput port P3, a seal member S2 (illustrated by a heavy line), which ismade of heat-resistance material and shaped like a sheet, is affixed toensure a sealing performance of the interior of the accommodationportion 9.

In addition, the input port P3 and the core part 5 are arranged in sucha way that the central axis X1 (illustrated in FIG. 9 (b)) of the inputport P3 and the core part 5 of the second heat exchanger 2 areorthogonal to each other.

Incidentally, the input port P1 and the second heat exchanger 2 arediagonally arranged in the first embodiment, to which the presentinvention is not limited. In addition, the second heat exchanger 2 maybe fixed on an inner wall of the projecting portion 11 by usingnot-shown brackets.

As shown in FIG. 6 to FIG. 9, a discharge pipe 20 extending below isprovided on the bottom portion of the projecting portion 11 of theaccommodation portion 9, in particular on the collection portion (10)side of the second heat exchanger 2 of the projecting portion 11, so asto communicate with the projecting portion 11 of the accommodationportion 9.

Further, as shown in FIG. 1, a discharge pipe 21 extending below isprovided on the bottom portion of the divided body 8 so as tocommunicate with the intermediate divided body 7.

The tank 4 is formed as a hollow body shaped like a rectangle with arectangular cross section, and the corresponding end portions of thetubes 5 a are inserted in and fixed to the inner side of the tank 4.

In addition, as shown in FIG. 1, an output port P4 is provided on theouter side of the tank 4 to bent rearward and project in the obliquedirection so as to communicate with the interior of the tank 4.

In addition, as shown in FIG. 10, insertion members 30 are inserted inand fixed to the end portions of the tubes 5 c that are inserted in andfixed to the intermediate divided body 7 in the plurality of tubes 5 a.

As shown in FIG. 11 (a), the insertion members 30 are entirely formedlike a letter U, and engagement portions thereof 30 b are respectivelyformed to project toward the outer side from the base portions of theinsertion portions 30 a, 30 a facing to each other of the letter U.

Further, as shown in FIG. 11 (b), the insertion portions 30 a, 30 a ofthe insertion member 30 are inserted in the tubes 5 c and eachengagement portion 30 b is engaged with the end portion of the tube 5 c,so that the insertion members 30 are inserted in and fixed to the tubes5 c.

In addition, clearance O1 are formed between the end portions of thetubes 5 c and the insertion members 30.

The entire construction members of the compound type heat exchanger A1of the first embodiment are made of metal material such as aluminum. Atleast one side of the joined portion of each construction memberincludes a brazing sheet or a brazing material formed by coating orpasting flux in advance.

Then, after the entire construction members of the first heat exchanger1 are temporally assembled in advance except the second heat exchanger 2and the input port P3, it is heat-treated to join the connecting portionof each construction member by brazing to be integrally formed.

On the other hand, after the entire construction members of the firstheat exchanger 1 are temporally assembled in advance, it is heat-treatedto join the connecting portion of each construction member by brazing tobe integrally formed.

Next, an engine cooling circuit 22 and a turbocharger circuit 23, whichuse the compound type heat exchanger A1 of the first embodiment, will bedescribed.

As shown in FIG. 12, in the engine cooling circuit 22, an engine A2, aradiator A3, a thermostat A4 and a water pump A5 are connected tocirculate coolant as a flowing medium through passages a1 to a4.

In addition, the passage a5 is provided to be arranged parallel to theradiator A3, thereby bypassing it.

Further, the passage a6 branching from the passage a1 is connected withthe input port P1 of the second heat exchanger 2 of the compound typeheat exchanger A1, while the passage a7 branching from the passage a2 isconnected with the output port P2 of the second heat exchanger P2.

The turbocharger circuit 23, using the air as a flowing medium, isequipped with the compound type heat exchanger A1, the engine A2, aturbocharger A6, an EGR cooler A7 and so on.

The upstream side of the compressor of the turbocharger A6 is connectedwith the passage a8, and the downstream side thereof is connected withthe input port P3 of the first heat exchanger 1 of the compound typeheat exchanger A1 through a passage a9.

The output port P4 of the compound type heat exchanger A1 is connectedwith not-shown intake ports of the engine A2 through a passage a10 (anintake manifold).

In addition, not-shown exhaust ports of the engine A2 is connected withthe upstream side of the turbine of the turbocharger A6 through apassage a11 (an exhaust manifold).

Further, the downstream side of the turbine of the turbocharger A6 isconnected with a passage a12.

Further, the upstream side of the EGR cooler A7 is connected with thepassage a11 through a passage a13, while the downstream side thereof isconnected with a passage a7 through a passage a14.

Further, not-shown check valves are provided at appropriate positions inthe passage a5 and other passages.

Next, the operation of the compound type heat exchanger of the firstembodiment, the engine cooling circuit 22 and the turbocharger circuit23 will be described.

<As to the Operation of the Engine Cooling Circuit and the TurbochargerCircuit that Use the Compound Type Heat Exchanger>

In the thus-constructed compound type heat exchanger A1, as shown inFIG. 12, in a case where the temperature of the coolant is equal to orlower than a certain temperature before the engine A2 is warmed up (whenthe temperature of the coolant is low), the thermostat A4 closes thepassage a2 in the engine cooling circuit 22, so that the coolantdischarged from the engine A2 flows to the passage a1→the passage a5→thepassage a3→the water pump A5→the passage a4 in these order, and itreturns to the engine A2.

When the temperature of the coolant exceeds the certain temperatureafter the engine A2 is warmed up (when the temperature of the coolant ishigh), the thermostat A4 opens the passage a2, so that the coolantdischarged from the engine A2 flows to the passage a1→the radiatorA3→the passage a2→the thermostat A4→the passage a3→the water pump A5→thepassage a4 in these order, and it returns to the engine A2. In thisoperation, the coolant at high temperature of approximately 80° C. (in acase of large vehicles) is cooled down to approximately 60° C. (in acase of the large vehicles) due to heat exchange with the airflowgenerated when the vehicle runs or the airflow generated by a fan 24while it passes through the radiator A3. Thus the engine A2 can becooled.

In addition, a part of the coolant in the passage a1, first, flows inthe input port P1 of the second heat exchanger 2 through the passage a6.Subsequently, the coolant that flows in the input port P1 of the secondheat exchanger 2 flows in the first chamber R1 of the tank 13, and thenit flows to the chamber R2 of the tank 14 and the chamber R3 of the tank13 in this order through the corresponding tubes 15 a, then beingdischarged to the passage a7 through the outlet port P2.

In the turbocharger circuit 23, the intake air that is sucked into thepassage a8 through a not-shown air duct and a not-shown filter ischanged to have a high-temperature and pressure state by the compressorof the turbocharger A6, and then it flows in the input port P3 of thefirst heat exchanger 1 through the passage a9.

Subsequently, the intake air at high temperature of approximately 170°C. (in a case of the large vehicles) flowing in the input port P3 of thefirst heat exchanger 1 flows in the accommodation portion 9 to be cooleddown due to the heat exchange with the coolant flowing in the tubes 15 awhile it passes through the core part 15 of the second heat exchanger 2,then flowing in the tank 3 through the collection portion 10.

Then, the intake air that flows in the tank 3 is cooled down toapproximately 40° C. (in a case of the large vehicles) due to the heatexchange with the airflow generated when the vehicle runs or the airflowgenerated by the fan 24 while it flows in the tank 4 through the tubes 5a.

The intake air that flows in the tank 4 is discharged to the passage 10(the intake manifold) through the output port P4, and then it flows inthe intake ports of the engine A2. Therefore, the turbo-chargeefficiency of the engine A2 increases to improve the output power of theengine.

The intake air introduced in the engine A2 changes to the exhaust gasand passes through the passage a11 to drive the turbine of theturbocharger A6, and then it is discharged to the exterior through thepassage a12 (the exhaust manifold) and an exhaust system such as anot-shown a catalyst for purifying the exhaust gas and a muffler.

In addition, a part of the exhaust gas in the passage a11 (the exhaustmanifold) flows in the EGR cooler A7 through the passage a13, and it iscooled down due to the heat exchange with a flowing medium in anot-shown sub-radiator. Then, the exhaust gas returns to the passage a8through the passage a14.

Thus, in the first embodiment, the high-temperature heat can be removedby introducing the part of the coolant of the engine A2 to the secondheat exchanger 2 and cooling the intake air of the first heat exchanger1 before it flows in the core part 5.

Therefore, heat shock to each portion, due to extreme lowering oftemperature of the intake air, can be avoided by the intake air beingcooled down in stages by the first heat exchanger 1. In addition,effective cooling by aid to cool the core part 5 can be performed.

In addition, the part of the exhaust gas is cooled down by the EGRcooler A7, and then it returns to the passage a8. Therefore, the exhaustgas can be purified by introducing the unburned components contained inthe exhaust gas into the engine A2 again.

Further, in the first embodiment, since the exhaust gas discharged fromthe EGR cooler A7 is returned to the passage a8 at the upstream side ofthe compressor 36 a of the turbocharger A6, the EGR ratio can be sethigher relative to a case where it is returned to the passage a10 (theintake manifold).

<As to Cooling of the Intake Air by the Second Heat Exchanger>

In the first embodiment, as described above, the input port P3 and thecore part 5 are arranged in such a way that the central line X1 of theinput port P3 and the core part 5 of the second heat exchanger 2 areorthogonal to each other.

Therefore, it becomes easier for the intake air (indicated by brokenarrows) flown in the projecting portion 11 through the input port P3 topass through the core part 5 of the second heat exchanger 2, and therebythe hot air can be prevented from accumulating in a space at the inputport (3) side of the second heat exchanger 2. Thus the intake air can besmoothly cooled.

<As to the Temperature Homogenization of the Intake Air>

Herein, there is a possibility of the deterioration of the root portionsand others of the tubes because heat stress occurs due to thetemperature distribution of the core part in a case where thetemperature of the intake air flowing in the tubes of the first heatexchanger are different from each other in tubes.

Therefore, in the prior invention, the core part of the second heatexchanger needs to be arranged in a state where it is arranged near andfaces to all the tubes as the second heat exchanger is arranged in thetank of the first heat exchanger. This causes the second heat exchangerto be unnecessarily larger in size.

Compared with this, in the compound type heat exchanger of the firstembodiment, the second heat exchanger 2 is placed in the accommodationportion 9 of the divided body 7, and accordingly the intake air can flowin all the tubes 5 a after the temperature of the intake air passingthrough the second heat exchanger 2 becomes uniform in the accommodationportion 9.

Therefore, the second heat exchanger 2 can be downsized to a largeextent, without generating the heat stress due to the temperaturedistribution of the core part 5.

On the other hand, in the prior invention, the temperature distributionoccurs in the flowing medium of the first heat exchanger after itexchanges heat when passing through the second heat exchanger, andconsequently the heat stress occurs due to the temperature distributionof the core part. Accordingly, there is a possibility of deteriorationin the durability of the core part of the first heat exchanger.

Compared with this, in the compound type heat exchanger of the firstembodiment, the accommodation portion 9 is provided to project outwardlyfrom the tank 3 though the collection portion 10 having narrow passages10 a, and the second heat exchanger 2 is arranged in the accommodationportion 9.

Therefore, the intake air that passes through the second heat exchanger2 can be mixed up in the narrow passages 10 a of the collection portion10 and the accommodation portion 10 to have uniform temperature and thento flow in the tank 3.

Accordingly, the intake air can flow through each tube 5 a at the sametemperature, and thereby the generation of the heat stress due to thetemperature distribution of the core part 5 can be avoided.

<As to the Flow Amount of the Flowing Medium that Flows to Each Tube ofthe First Heat Exchanger>

In the first embodiment, as explained with reference to FIGS. 10 and 11,the insertion members 30 are inserted in and fixed to the end portionsof the divided body 7.

In addition, the clearances O1 are formed between the end portions ofthe tubes 5 and the insertion members 30.

Therefore, as shown in FIG. 10, most of the intake air (indicated bybroken arrows in FIG. 10) that flows in the divided body 7 from theaccommodation portion 9 through the collection portion 10 can flow alongthe longitudinal direction of the tank 3 and flow in each tube 5 a.

In addition, a part of the intake air (indicated by broken arrows inFIG. 10) that flows in the tank 3 can flow in the tubes 5 a through theclearances O1.

Accordingly, the insertion members 30 can regulate the flow amount ofthe intake air in the tubes 5 c of the intermediate divided body 7 wherethey are arranged near the inlet toward the tank 3 of the intake air anda large amount of the intake air could easily and swiftly flow therein.

In other words, in the first embodiment, the clearances O1 are set sothat the flow amount of the intake air that flow in the tubes 5 c can beequal to or less than that in the other tubes 5 a.

Thus, in the first embodiment, the flow amount of the intake air in eachtube 5 a can be uniform, and thereby the temperature distribution can beuniform.

Incidentally, the insertion members 30 may be provided at the tank (4)side end portions of the tubes 5 c.

In addition, the insertion members 30 are attached to all of the tubes 5c in the first embodiment, to which the present invention is notlimited. The number of the tubes 5 c and the insertion members 30 may beset appropriately.

Further, in some cases, a so-called dead tube, which completely blockscommunication of the flowing medium of the tubes 5 c, may be employed.

<As to Heat Expansion and Construction of the Second Heat Exchanger>

The coolant that flows through the second heat exchanger 2 is thecoolant of the engine A2, and accordingly its temperature changesbetween an outside temperature and approximately 80° C.

Consequently, the second heat exchanger 2 expands and contracts due tothe heat, and accordingly there is a possibility that the adverse affectof heat stress due to heat expansion and construction may occur in acase where the second heat exchanger 2 is fixed on a wall portion in theprojecting portion 11 by using brackets or others.

Compared with this, in the first embodiment, the second heat exchanger 2is arranged in the projecting portion 11 in the obliquely suspendedstate, and the gap is formed between the second heat exchanger 2 and thewall portion in the projecting portion 11. Therefore, the second heatexchanger 2 can be fixed without unnecessary restraint, and thereby theadverse affect of the heat stress can be avoided by mainly expanding andcontracting the tubes 15 in the longitudinal direction due to the heat.

<As to Condensed Water>

In the first embodiment, the exhaust gas that is discharged from the EGRcooler A7 is returned to the passage a8 at the upstream side of thecompressor 36 a of the turbocharger A6. Accordingly, the EGR ratio canbe increased, but the water existed in the exhaust gas is contained inthe intake air that is introduced to the first heat exchanger 1.

The water is acid, which might have the adverse affect on each portionof the first heat exchanger 1 and the second heat exchanger 2.

Compared with this, in the first embodiment, as shown in FIG. 13, thewater contained in the intake air and the water (indicated by analternate long and two short dashed arrow in FIG. 13) generated due tothe intake air that is cooled in the second heat exchanger 2 aredischarged below through the discharge pipe 20 from the bottom portionof the accommodation portion 9.

Therefore, the condensed water can be discharged at an earlier stagewhere the intake air flows in the first heat exchanger 1, and therebythe adverse affect on the first heat exchanger 1 and the second heatexchanger 2 due to the condensed water can be avoided.

Incidentally, the opening end portion of the divided body 8 of the firstembodiment is connected with the bottom portion of the divided body 7 ina state where the opening end portion of the divided body 8 is insertedin the bottom portion of the divided body 7, and accordingly there is nopossibility that the condensed water may accumulate on the bottomportion of the accommodation portion 9 and leak toward the divided body(8) side.

Further, as shown in FIG. 1, the discharge pipe 21 extended below isprovided on the bottom portion of the divided body 8 to communicate withthe divided body 7, and therefore the condensed water (indicated by analternate long and two short dashed arrow in FIG. 1) accumulating in thetank 3 can be discharged toward the exterior thereof through thedischarge pipe 21.

Incidentally, not-shown hoses, which extend down to the under floor ofthe vehicle, are attached to the lower end portions of the dischargepipes 20, 21. Incidentally, the diameters of the discharge pipes 20, 21are small, while the discharge pipes 20, 21 may be provided with valves.

<As to Design Freedom of the First Heat Exchanger and the Second HeatExchanger>

In the first embodiment, the tank 3 is composed of the plurality ofdivided bodies 6 to 8 that are connected along the longitudinaldirection of the tank 3, and the accommodation portion 9 is provided inthe divided body 7. The second heat exchanger 2 is arranged in theaccommodation portion 9, on which the input port P3 is provided.

Therefore, the divided body 7 provided with the accommodation portion 9can employ common use parts, and in this case, only the design change ofthe other divided bodies 6, 8 can easily accommodate many kinds of thefirst exchangers different in the heights of their core parts.Alternatively, only the design change of the divided body 7 with theaccommodation portion 9 can accommodate many kinds of the second heatexchangers 2 with different sizes.

In addition, the input port P3 is fixed to the accommodation portion 9detachably therefrom from the exterior side thereof, and therefore theinput port P3 can be easily changed in an angle, a diameter, aconfiguration of its end portion, and others.

Incidentally, the opening portion 11 a of the projecting portion 11 ofthe first embodiment is formed to be larger to some extent than the borediameter of the input port P3, and the opening portion 11 a is contactedand connected with the base portion of the inlet port P3 to communicatewith each other in a state where they face to each other. Therefore,only the design change of the input port P3 can perform the designchange of reducing or increasing in size of its bore diameter.

Thus, in the first embodiment, the design freedom of the first heatexchanger 1 and the second heat exchanger 2 can be increased.

<As to Downsizing of the First Heat Exchanger>

In the prior invention, since there is a need to accommodate the entiresecond heat exchanger in the tank of the first heat exchanger, a largespace is needed inside the tank, and consequently the size of a corepart of the first heat exchanger is limited.

Therefore, there is much loss because of the downsizing of the core partof the first heat exchanger.

Compared with this, in the first embodiment, the second heat exchangeris arranged in the accommodation portion 9, and therefore the designfreedom of especially the size in a width direction of the tank 3 can beincreased without the need of a large space in the tank 3.

In addition, the accommodation portion 9 has the shape projecting fromthe tank 3 in the width direction through the collection 10, andtherefore the design freedom of the layout for arranging its peripheralmembers can be increased by reducing the height of the tank 3.

<As to a Maintenance Performance of the Second Heat Exchanger>

The second heat exchanger 2 is fixed to the accommodation portion 9detachably therefrom from its exterior side.

Therefore, when the second heat exchanger 2 is replaced, repaired,checked and so on, the second heat exchanger 2 can be easily brought outof the accommodation portion 9 by removing the bolts B2. Accordingly, itprovides an excellent maintenance performance.

The effects of the composite type heat exchanger A1 of the firstembodiment will be described below.

(1) The first heat exchanger 1 is equipped with the pair of long tanks3, 4 that are arranged the certain distance apart from each other andthe core part 5 including the tubes 5 a and the fins 5 b that arealternately piled up between the both tanks 3, 4. The tank 3 is composedof the plurality of the divided bodies 6 to 8 that are connected alongthe longitudinal direction of the tank 3. The divided body 7 is providedwith the accommodation portion 9 having the shape projecting outwardlyto communicate with the certain divided body 7. The second heatexchanger 2 is arranged inside the accommodation portion 9, and theinput port P3 is provided on the accommodation portion 9. The heat isexchanged between the intake air of the first heat exchanger 1 thatflows in the accommodation portion 9 and the coolant of the second heatexchanger.

Therefore, the design freedom of the first heat exchanger 1 and thesecond heat exchanger 2 can be increased.

For example, the intermediate divided body 7 provided with theaccommodation portion 9 can employ common use parts, and only the designchange of the other divided bodies 6, 8 can accommodate many kinds offirst heat exchangers 1 with different heights of the core parts 5.Alternatively, only the design change of the intermediate divided bodywith the accommodation portion 9 can accommodate many kinds of thesecond heat exchangers with different sizes.

(2) The input port P3 is fixed to the accommodation portion 9 detachablytherefrom from its exterior side.

Therefore, it can accommodate input ports P3 with various angles,diameters and others.

(3) The second heat exchanger 2 is fixed to the accommodation portion 9detachably therefrom from its exterior side.

Therefore, the maintenance performance of the second heat exchanger 2can be improved.

(4) The second heat exchanger 2 is equipped with the pair of long tanks3, 4 that are arranged the certain distance apart from each other andthe core part 5 including the tubes 5 a and the fins 5 b that arealternately piled up between the both tanks 3, 4. The central line ofthe connection port and the core part 5 are arranged in such a way thatthey are orthogonal to each other.

Therefore, the heat exchange between the first exchanger 1 and thesecond heat exchanger 2 can be effectively performed.

(5) The accommodation portion 9 is provided to have the shape projectingin the width direction of the certain divided body 7.

Therefore, the tanks 3, 4 can be prevented in growing in the sizes inthe left and right direction thereof, and thereby the design freedom ofthe layout for arranging its peripheral parts can be increased.

(6) The input port P3 is the inlet port for the intake air of the firstheat exchanger 1, and the intake air of the first heat exchanger 1 iscooled down due to the heat exchange between the intake air in the firstexchanger 1 and the coolant in the second heat exchanger 2.

Therefore, the intake air in the first exchanger 1 can be cooled instages, the heat shock due to sudden fall of the temperature of theintake air can be prevented from occurring, and the coolability of thefirst heat exchanger 1 can be improved.

(7) The accommodation portion 9 is formed at the certain divided body(7) side of the second heat exchanger 2 with the collection portion 10forming the narrow passages 10 a.

Accordingly, the intake air can flow in the tubes 5 a of the core part 5after the intake of the first heat exchanger 1 that exchanges its heatwith the second heat exchanger 2 is uniformed in temperature by beingmixed up in the collection portion 10.

Therefore, the heat stress due to the heat distribution of the core part5 can be prevented from occurring, so that a crack in the tubes 5 a, 15a or a crack at tube holes 6 a, 7 a, 8 a due to the heat shock can beavoided, and thereby the durability of the core part 5 and thedurability of the first heat exchanger can be improved.

(8) The first heat exchanger 1 is the intercooler, and the flowingmedium of the second heat exchanger is the coolant of the engine coolingcircuit 22.

Therefore, it is preferable to apply the first heat exchanger 1 to theintercooler whose demand for cooling specification of recent highpowered engines becomes higher.

In addition, a combination of the optimum thermal relationships betweenflowing mediums as heat exchange mediums can be realized.

(9) The discharge pipe 20 capable of discharging the condensed water isprovided on the bottom portion of the accommodation portion 9.Therefore, the adverse affect on the first heat exchanger 1 and thesecond heat exchanger 2 due to the condensed water can be avoided.

(10) The discharge pipe 21 capable of discharging the condensed water isprovided on the bottom portion of the tank 3.

Therefore, the adverse affect on the first heat exchanger 1 and thesecond heat exchanger 2 due to the condensed water can be suppressed tothe minimum extent.

Second Embodiment

Hereinafter, a second embodiment of the present invention will bedescribed.

Incidentally, in a compound type heat exchanger of the secondembodiments, the construction members similar to those of the firstembodiment are indicated by the same reference numbers and thosedescriptions are omitted. Only the differences will be in detaildescribed.

As shown in FIGS. 14 and 15, in the compound type heat exchanger, adeformed portion 31, where an end portion of a tube 5 c is decreased indiameter, is employed instead of the insertion member 30 that hasexplained in the compound type heat exchanger of the first embodiment.

In addition, the end portion of the deformed portion 31 is formed withan opening portion O2 instead of the clearance O1 that has beenexplained in the first embodiment.

Therefore, in the second embodiment, the flow amount of the intake airflowing in the tubes 5 c of a divided body 7 can be prevented frombecoming larger than that in the other tubes 5 a, and the operation andeffects similar to those of the first embodiment can be obtained.

In addition, the deformed portion 31 can be formed by a simple workwhere the end portion of the tube 5 c is deformed by a jig or the liketo decrease its diameter, without increasing the number of parts.

Incidentally, in some cases, a so-called dead tube, where the deformedportion 31 is completely caved to remove the opening portion O2, may beemployed.

Next, the compound type heat exchanger of the second embodiment has thefollowing effects in addition to those effects.

(12) A flow adjustment means is formed by the deformed portions 31 wherethe end portions of the tubes 5 c corresponding to the divided body 7 todecrease its diameter.

Therefore, it can easily obtain the effect similar to those of the firstembodiment without using another member.

Although the embodiments have been described, the present invention isnot limited to the above-described embodiments, and a design change andthe like may be resorted to without departing from the scope of thepresent invention.

For example, the first heat exchanger 1 may be a radiator, the secondheat exchanger 2 may be an oil cooler, and thus the present inventionmay be applied to a so-called radiator with a built-in oil cooler.

In this case, similarly to the radiator described in known JapanesePatent Application Laid-Open Publication No. 2008-32242, the input portP3 is an outlet port of the flowing medium of the first heat exchanger(the radiator), and the flowing medium of the second heat exchanger (theoil cooler) is cooled due to heat exchange between the flowing medium(the coolant) of the first heat exchanger (the radiator) and the flowingmedium (the oil) of the second heat exchanger (the oil cooler).

In addition, material of each construction member may be selectedappropriately, and its fixing method may be changed according to theselected material.

Further, the number of the divided bodies of the tank 3, theseconnecting structure and others may be set appropriately.

For example, the divided bodies may be connected with each other byusing bolts.

Further, a portion of the tank 3 may be made of resin material.

Further, in the embodiments, the accommodation portion 9, which projectsrearward through the collection portion 10 extending in the left andright direction from the divided body 7, is employed, and the directionof the displacement of the collection portion 10 and the accommodationportion 9 may be set appropriately.

1. A compound type heat exchanger comprising: a first heat exchangerhaving a pair of tanks arranged a certain distance apart from each otherand a core part having a plurality of tubes between the tanks; and asecond heater embodiment, wherein at least one of tanks is constitutedof a plurality of divided bodies that are divided and connected along alongitudinal direction of the at-least one of the tanks, wherein acertain divided body of the plurality of divided bodies is provided withan accommodation portion that projects outwardly to be connected withthe certain divided body so that a flowing medium of the first heatexchanger can flow to the certain divided body, wherein the second heatexchanger is arranged in the accommodation portion, wherein theaccommodation portion is provided with a connection port as a gateway ofthe flowing medium of the first heat exchanger, and wherein heat isexchanged between the flowing medium of the first heat exchanger thatflows thorough the accommodation portion and a flowing medium of thesecond heat exchanger.
 2. The compound type heat exchanger according toclaim 1, wherein the connection port is fixed to the accommodationportion detachably therefrom from an exterior side of the accommodationportion.
 3. The compound type heat exchanger according to claim 1,wherein the second heat exchanger is fixed to the accommodation portiondetachably therefrom from an exterior side of the accommodation portion.4. The compound type heat exchanger according to claim 1, wherein thesecond heat exchanger is equipped with a pair of tanks arranged acertain distance apart from each other and a core part having aplurality of tubes between the tanks, and wherein the connection portand the core part are arranged in such a way that a central line of theconnection port and the tubes of the core part of the second heatexchanger are orthogonal to each other.
 5. The compound type heatexchanger according to claim 1, wherein the accommodation portionprojects in a width direction of the certain divided body.
 6. Thecompound type heat exchanger according to claim 1, wherein theconnection port is an inlet port of the flowing medium of the first heatexchanger, and wherein the flowing medium is cooled due to heat exchangebetween the flowing medium of the first heat exchanger and the flowingmedium of the second heat exchanger.
 7. The compound type heat exchangeraccording to claim 6, wherein the first heat exchanger is anintercooler, and wherein the flowing medium of the second heat exchangeris a coolant of an engine cooling circuit.
 8. The compound type heatexchanger according to claim 7, wherein a first discharge portion thatis capable of discharging condensed water is provided on a bottomportion of the accommodation portion.
 9. The compound type heatexchanger according to claim 7, wherein a second discharge portion thatis capable of discharging condensed water is provided on a bottomportion of the at-least one of tanks.
 10. The compound type heatexchanger according to claim 1, wherein the connection port is an outletport of the flowing medium of the first heat exchanger, and wherein theflowing medium of the second heat exchanger is cooled due to heatexchange between the flowing medium of the first heat exchanger and theflowing medium of the second heat exchanger.
 11. The compound type heatexchanger according to claim 10, wherein the first heat exchanger is aradiator, and wherein the second heat exchanger is an oil cooler. 12.The compound type heat exchanger according to claim 1, wherein theaccommodation portion communicates with the divided body different fromthe certain divided body of the plurality of divided bodies through acollection portion formed with an opening-space reduced passage.
 13. Thecompound type heat exchanger according to claim 12, wherein anadjustment means is provided so that the adjustment means can regulate aflow amount of the flowing medium that flows in the tubes correspondingto the certain divided body to be not more than a flow amount of theflowing medium that flows in the other tubes.
 14. The compound type heatexchanger according to claim 13, wherein the adjustment means is aninsertion member that is inserted in and fixed to end portions of thetubes corresponding to the certain divided body.
 15. The compound typeheat exchanger according to claim 13, wherein the adjustment means is adeformed portion formed by decreasing opening space of an end portion ofthe tubes corresponding to the certain divided body.
 16. The compoundtype heat exchanger according to claim 4, wherein the connection port isan inlet port of the flowing medium of the first heat exchanger, andwherein the flowing medium is cooled due to heat exchange between theflowing medium of the first heat exchanger and the flowing medium of thesecond heat exchanger.
 17. The compound type heat exchanger according toclaim 5, wherein the connection port is an inlet port of the flowingmedium of the first heat exchanger, and wherein the flowing medium iscooled due to heat exchange between the flowing medium of the first heatexchanger and the flowing medium of the second heat exchanger.
 18. Thecompound type heat exchanger according to claim 4, wherein theconnection port is an outlet port of the flowing medium of the firstheat exchanger, and wherein the flowing medium of the second heatexchanger is cooled due to heat exchange between the flowing medium ofthe first heat exchanger and the flowing medium of the second heatexchanger.
 19. The compound type heat exchanger according to claim 5,wherein the connection port is an outlet port of the flowing medium ofthe first heat exchanger, and wherein the flowing medium of the secondheat exchanger is cooled due to heat exchange between the flowing mediumof the first heat exchanger and the flowing medium of the second heatexchanger.
 20. The compound type heat exchanger according to claim 10,wherein the accommodation portion communicates with the divided bodydifferent from the certain divided body of the plurality of dividedbodies through a collection portion formed with an opening-space reducedpassage.